Pump actuating systems



Nov. 27, 1962 R. H. HILL PUMP ACTUATING SYSTEMS 7 Sheets-Sheet 1 FiledJune 1, 1959 Faber! 22 77714;

e Jf/Zor/Iey V Nov. 27, 1962 R. H. HILL 3,065,704

PUMP ACTUATING SYSTEMS Filed June 1, 1959 7 Sheets-Sheet 3 76 INVENTOR.

R. H. HILL 3,065,704

7 Sheets-Sheet 4 INVENTOR. r?05er/ .4? 14 174 M fa aways Nov. 27, 1962PUMP AC'TUATING SYSTEMS Filed June 1, 1959 a in:

mm mu NU R. H. HILL PUMP ACTUATING SYSTEMS Nov. 27, 1962 7 Sheets-Sheet7 Filed June 1, 1959 Y IN V EN TOR /PaAerz [K i B ire 3,965,764 PUMFAETUATTNG EYSTEMS Rohert H. Hill, Fort Wayne, Ind, assignor toParker'sburg Rig and Reel Company, Cofieyvilie, Kans., a corporation ofWest Virginia Filed June 1, H59, Ser. No. 817,173 7 Claims. (Cl.1023-46) This invention is directed to improvements in pumping systemsand particularly relates to actuators for vertically reciprocating pumpssuch as are commonly used in oil wells.

In deep well pumps, such as oil well pumps, it is highly desirable toprovide an actuating mechanism which provides a long stroke for the pumpand at the same time can be used at an economical price. In extremelydeep wells, the stretch of the actuating rod for the pump necessitates along stroke for the proper actuation of the pump. Furthermore a longstroke is desirable from the standpoint of minimizing wear, since a longstroke unit can operate at a slower speed than a short stroke unit forthe same production capacity.

Prior actuating systems have oftentimes taken the form of motor drivenoscillating beams which are connected to the pump actuating rod forreciprocation thereof. To obtain a long stroke, the beam and other partsof the system must be quite large and cumbersome. Some long stroke pumpactuating systems have taken the form of hydraulic cylinders suppliedwith fluid from an hydraulic pump but these systems are inefiicient andrequire an unduly large amount of power for their operation.

The present invention aims to alleviate these disadvantages by theconstruction of a relatively inexpensive and etrlcient reciprocatingpump actuating mechanism which is arranged so as to provide an extremelylong stroke, if desired, while requiring a minimum amount of operatorattention for the operation of the pump.

One object of the invention is to provide a pump actuating system whichdoes not require plugging or a reverse flow of current to the motor inorder to overcome the inertia of the motor and stop the rotation of themotor, whether the motor is energized or de-energized, as the pumpapproaches the end of its stroke.

Another purpose of the present invention is the provision of an improvedcontrol system for electric motor driven vertically reciprocating pumps,which system allows proper time for the pump to fill at the bottom ofthe reciprocating stroke and a well filling time interval at the upperportion of the stroke.

Another purpose of the present invention is the provision of novel andpractical means for retarding and decelerating the down stroke of avertically reciprocating pump while at the same time providingcirculation of lubricant through an actuating mechanism and providing acooling system for the lubricant.

Another purpose is to provide a novel balancing system for a verticallyreciprocating pump actuated by a double acting reversible motor.

In pumping systems of this general class, packing glands are ordinarilyassociated with the polish rod which is connected to the sucker rod ofthe pump and these packing glands must be located below the casing head.If one desires to minimize the above ground height of the unit, thegland must be embedded in the ground, where the problem of tighteningthe gland, which tends to work and become loosened with thereciprocating motion of the sucker rod, becomes difiicult. Packingglands of this class may also function to prevent leakage of lubricatingoil for the system along the rod and to prevent the iluid being liftedby the pump from working into the lubricating oil body which wouldcontaminate the lubricant. Accordingly, another purpose of the presentinvention is to provide novel, practical and efiicient means forproperly packing the polish rod of such a pump to prevent suchcontamination and leakage, and at the same time provide means forautomatically compensating for any wear or loosening of the gland whichmay occur during the working of the sucker rod.

Other objects and purposes will appear from time to time in the courseof the ensuing specification and claims when taken with the accompanyingdrawings in which:

FIGURE 1 is a diagrammatic view of a pump and pumping actuating systemembodying the present invention;

FlGURE 2 is a diagrammatic view of a control circuit usable with thesystem illustrated in FIGURE 1;

*IGURE 3 is a top view of the unit illustrated in FIG- URE 1 taken onthe lines 33 of FIGURE 4;

FIGURE 4 is an enlarged sectional illustration of another portion of thesystem illustrated in FIGURE 1;

FIGURE 5 is a sectional illustration of FIGURE 3 taken on the sectionlines 5 5 of FIGURE 3;

FIGURE 6 is an enlarged sectional illustration of another portion of themechanism illustrated in FIGURE 1;

FIGURE 7 is an enlarged sectional illustration of still another portionof the mechanism illustrated in FI URE 1 and particularly illustratingpackaging means for the polish rod usable with the present invention;

FIGURE 8 is a diagrammatic view of another embodiment of the invention;

FIGURE 9 is a diagrammatic view of a control circuit utilized in theembodiment of FIGURE 8;

FIGURE 10 is an enlarged sectional view of a portion of the systemillustrated in FIGURE 8; and

FIGURE 11 is an enlarged sectional view of the upper portion of theactuator housing.

in the drawings and specification, like elements are designated by likecharacters throughout.

With particular reference now to the drawings and in the first instanceto FIGURE 1, 2i designates a well casing that extends vertically intothe ground. Mounted within the casing and adapted for reciprocatingmovement therein is a polish rod diagrammatically represented at 21which is connected to the sucker rod 21a of the pump. The sucker rod 21ais adapted through vertical reciprocation thereof to actuate a pumpdiagrammatically indicated at 2.2 and lift fluid through a tube 23surrounding the polish rod 21 to and through a manifold 24. The manifold24 includes a discharge outlet 25 therein. The manifold 24 is mountedupon a head 26 which in turn is mounted upon the casing 2b. The head 26may include a gas outlet 27. It should be understood that the showing ofthe sucker rod, pump, and casing are intended to be representative ofconventional pumping systems as are Well known to the art.

ln accordance with the present invention an upstanding actuator housing2-8 is adapted to be seated upon and fixed to the upper end of themanifold 24. The housing 28 includes an enlarged transmission portion 29which houses a rotatable driving member 30 and a verticallyreciprocating driven member 31, the driving member and driven memberforming a screw and nut type of drive. The driven member 31 is coupledto the polish rod in a manner to be explained in ensuing portions ofthis specification. The driving member so has a bevel gear 32 coupledthereto and is driven from a pinion gear 33 which is supported onbearings 33a and which receives power from the output side of a motor34. The motor 34 is mounted on the side of an auxiliary housing 35 whichmay house a fluid coupling 3-6 for transmitting power from the outputshaft of the motor to the pinion gear 33. The driving member 3t), aswill be seen best in FIGURE 5, may be coupled to the bevel gear 32through the use of a coupling ring or hub 320 which is keyed to thedriving member 30 cal directions.

aoea'roa and which in turn is bolted to the bevel gear 32 and bolted toa hub 32b for the bevel gear 32. The hub 32!; is rotatably supported ontapered roller bearings 32c, the outer races of which are fixed to abearing support 32d on the inner wall of the housing.

In order to minimize friction, a rolling connection is provided betweenthe driving member 30 and driven member 31. The driving member 39includes a plurality of passages 38 which are formed on the innersurface of a central, longitudinally extending aperture therethrough andare spirally formed in the manner of a screw thread. The reciprocatingdriven member 31 includes spirally formed grooves 39 on the exteriorsurface thereof and through substantially the entire length thereof. Thegrooves 39 on the driven member 31 are of the same general size andpitch as the grooves on the member 31 Antifriction means in the form ofa plurality of spherical members 4% bring about a driving connectionbetween the driving member 30 and the reciprocable driven member 3 9.The member 30 includes a return passage 41 which spans at least twogrooves therein so that the entire space within the passage 11 and thegrooves between the ends thereof is filled with the balls 4t), suchballs being in rolling contact with one another and with the grooves ofthe driving member and driven member. Thus, during rotation of themember 39, the balls 4% may circulate in the race provided therefor inthe member 3% and member 39 and through the passage 41 and during suchrolling circulation, the driven member 39 Will be reciprocated in verti-Two complete sets of rolling members 44' and return passages 41 may beprovided in the assembly, as illustrated in FIGURE 5.

Means are provided for preventing rotation of the member 31 duringrotation of the driving member 3b. This means takes the form of asplined guide 42 which is coupled to the upper end of the member 31, asseen best in FIGURE 4. The splined member 4 2 may includequadrilaterally spaced grooves and projections 43a in the surfacethereof, as seen best in FTGURE 3. The projections ride in recessesformed in the inner wall of the housing 28, as is seen best in FIGURE 3.The projections on the guide are spaced a small distance from the innersurfaces of the recesses.

The splined member 42 may rest upon a shoulder in the upper end of thedriven member 31 and may be held thereon by a locking assembly which mayinclude a locking ring 43 threaded onto the upper end of the member 31and lock washers 44 and d engaged with the ring 4 3, driven member 3-1and the splined member 42.

The invention includes a means for inducing a forced circulation of oilthrough the housing while at the same time providing a decelerated andcushioning action for the driven member 31 as the driven memberapproaches the end of its downward stroke. In order to attain this end,the driven member 31 includes a longitudinally extending passage 48which is formed therein so as to allow circulation of a lubricatingfluid from the bottom of this member to the top thereof and then backthrough the housing. The enlarged portion 29 of the housing may befilled with lubricating fluid to a level somewhat above the level of thebevel gear 32, which level may be indicated from time to time by an oilgauge 49. The fluid may flow downwardly between the driven member 31 andthe inner wall of the hub 32b to the general level of the packing glandwhich appears in FIGURE 7. in this regard it should be noted that thelower end of the driven member 31 is connected to a piston-like member50 and the polish rod 21 may be threadably connected to the lower end ofthis piston-like member 5%) so that as the driven member 31 isreciprocated, the polish rod and sucker rod will be reciprocatedtherewith. The pistonlike member 5% has a generally cylindrical form andis slidingly received in a liner 51 which is fixed to a tube 52, whichin turn is spaced from a production tube 23 so as to define therebetweena passage for the upward flow of fluid to and through the dischargeoutlet 25. The tubes 52 and 23 may be supported on the productionmanifold 24.

The piston-like member includes a longitudinally extending passagewaytherein so as to allow flow of oil to the passageway 48 through thedriven member 31 and includes side passages and 56 that affordcommunication between the interior of the passage 54 and the spaceexterior to the piston 5%. Thus, as the driven member is moveddownwardly, oil displaced thereby may flow through the passages 55 and56 and upwardly through the passage 54 and the passage 48.

In order to progressively increase the resistance offered by the oil asthe piston and driven member move downwardly near the completion oftheir downward stroke, the inner wall of the liner 51 is taperedupwardly and outwardly so as to cooperate with the passages 55 and 56 ineffecting a valving action on the flow of fluid through the passages 55and 56. The taper to the liner 51 is such that at its lowermost pointits diameter corresponds quite closely to the external diameter of thepiston-like member 50. When the driven member 31 is near the upper limitof its movement, as when it is just commencing its downward movement,the piston 50 will be disposed above the liner 51 with the passages 55and 56 similarly disposed above the liner 51. Thus, during the majorityof the downward movement of the driven member 31 and piston 50, oil mayflow relatively freely through the passages 55 and 56 and will be forcedupwardly through the driven member 31 due to the displacement of the oilcaused by the downward movement of the piston and as the piston entersthe liner 51. As it continues its downward movement the available spacebetween the outer wall ofthe piston and the wall of the liner 51 isgradually restricted and the piston moves against a heavier resistanceoffered by the oil'beneath the piston. This resistance progressivelyincreases until the piston is at the lower limit of its downward strokewhere the restriction on the oil flow is greatest and the result is afinal cushioning of the downward stroke of the driven member. a

The driven member 31 carries a valving mechanism at a level above theplunger or piston-like member 50 which allows the free flow of oil asthe driven member 31 moves upwardly but then, on the down stroke, closesthe space through which the member 50 moves to the free communicationwith the main body of oil in the housing 29. This valving structureincludes a piston 58 which is fixed to and moves with the driven member31 and which includes passages 59 and 60 extending therethrough so as toallow flow of oil from above the piston to the space below. A valveretaining collar 61 is fitted onto the driven member 31 between themember 58 and member 50 and includes a spring 62 surrounding the member61 and biasing a valve closing member 63 into closing relation to thepassages 59 and 60. The valve closing member 63 may take the form of aring surrounding the collar 61 and having a flange which is adapted toseat against and close the passages 59 and 68' in the member 58. Thelower end of the spring 62 may be seated on the upper surface of anoutwardly extending flange 64 of the collar 61. The flange 64 may bespider-like in form so as to allow the passage of fluid therethrough.

This valving structure acts as a check valve in allowing free flow offluid through the passages 58 and 59 and to the space beneath the collar61 when the driven member 31 is moving upwardly but then as the drivenmember 31 commences its downward stroke the bias of the spring and theforce of the oil exerted in a valve closing direction on the member 63will close the passages 59 and 60 0 and thus trap oil beneath the member58 and beneath the member 513.

The collar 61 and piston 53 may be held in assembled relation on thedriven member 31 by means of a shoulder 65 formed on the member 31 andagainst which the upper surface of the piston 58 abuts and a lockingring 6-5 which spea /o4 is threaded onto the driven member 31 to providea shoulder against which the lower surface of the collar 61 abuts. Alock washer 67 may be positioned between the locking ring 66 and theupper surface of the piston-lik ber 59. The locking washer 7 may includea pr portion 63 which seats in a key-way 69 in the driven member, aprojecting portion '70 which seats in a keyway 71 in the member 50, anda projection 7=a fitting in a key-way in ring 66 so that the lockingring 66 and piston 59 are held unitarily together and against rotationon the driven member 31.

The piston 58 may include rings engaging the inner wall of the tube 52so as to preclude passage of oil between the piston wall and inner wallof the tube.

Means are provided for adjustable restricting the upward flow of oilthrough the driven member so that the downward speed of the drivenmember may be selected and adjusted in accordance with the desires ofthe user. This means takes the form of a needle valve assembly in theupper portion of the driven member 31 and which regulates the flow ofoil therethrough and out to and through the splined guide therefor. Aswill be seen best in FIGURE 4, the upper end of the driven member 31 hasa needle valve housing 73 mounted thereon. The needle valve housing 73may have a lower shouldered surface seating on the shoulder 74 of arecess in the member 31 and may be held fixed to the member 31 as bymeans of a retaining ring 75. This ring 7% is fixed to the housing '73at a point overlying the upper end of the member 31 and in a manner suchthat the ring is confined between an inwardly directed flange 76 of thelocking collar 43 and the upper end of the member 31. The needle valvehousing "72 includes a passage extending therethrough and generallyaligned with the passage d8 through the member 31. A needle valve 77 isthreaded into the needle valve housing 73 and includes a needle 73 inadjustably restricted relation to the lower end of the passagetherethrough. Aligned apertures are formed in the needle valve housing'73, member 31 and splined guide 42 as appear at '79 and 8% in FIGURE 4so that oil may pass from the passage in the needle valve housingthrough these passages 79 and 8% and down into the spaces between thesplined member and housing 28. The upper portion of the needle valveabove the passages 79 and 8b is in fluid-tight relation to the housing73. Thus, as the driven member 31 moves downwardly, oil may moveupwardly through the central passage 48, past the needle valve andthrough to passages 79 and S ll where it may then flow downwardlythrough the spaces between the splincd member and the housing for areturn to the main body of the lubricant in the enlarged portion of thehousing.

By suitably adjusting the needle valve 78, the rate of oil flow throughthe driven member is adjusted and hence the restricting or retardingeffect offered by the oil to the driven member during its entiredownward movement may be adjusted. In addition to the retarding actionthe system insures a circulatory flow of the lubricating fluid which notonly provides adequate lubrication for the splined fitting and thetransmission in the enlarged portion of the housing, but at the sametime provides cooling for the lubricant and hence cooling for thetransmission.

The upper end of the housing 28 may include a cap 81 which is threadedonto a cylindrical member 82 fixed to housing 2?. is upper end of theneedle valve 7 may include a handle 77a, as is seen in FIGURE 1, forsuitably adjusting the needle valve to provide the desired restrictingand speed regulating effect. The needle valve assembly may be locked inposition by means of a spring biased detent 82a which is selectivelyengageable with circumferentially spaced grooves 3221 thereby preventingturning of the valve due to vibration.

ln some cases, a check valve may be provided in the passage 54 or 2-3and arranged to allow the flow of lubricant upwardly through thesepassages on the downstroke of member 31. while preventing flow oflubricant and air through these passages on the upstroke of member 31.

The invention contemplates a self-tightening packing gland which, ifdesired, may be positioned beneath the ground and remaining effectivewithout requiring operator attention. In FIGURE 7 a packing glandhousing Rl is fitted in the tube with the central portion thereof inengagement with the tube 23. The central portion may be sealed with thetube 23 as by G-rings 9E. The upper end of the housing is fixed to theinner tube 52 as by threads $2.. The central portion of the housing hasa passage or passages 93 therethrough so as to allow the fluid lifted bythe pump to flow upwardly between the tubes 52 and 23 for consequentdischarge through the production manifold.

ln packing glands of this type, the gland must effectively seal thespace above the gland from the space below the gland. in a structure ofthe type illustrated, the pressure in the space above the gland mayreach several thousand pounds per square inch as the actuating rodreaches the lower extremity of its stroke. The pressure in the spacebelow the gland may be much lower so that the gland is subjected to ahigh ditterential pressure which tends to force lubricating fluiddownwardly along the rod. Furthermore, in a gland of this type, theproduction fluid, which has a pressure exceeding the dash pot pressureof near zero when the actuation member is near the top of its stroke andwhich is lifted in the space surrounding the polish rod, must be keptfrom Working along the rod and into the lubricating fluid withconsequent contamination thereof.

In order to minimize these problems, the packing of the invention usesupper and lower glands each of which is tightened against the housingand rod independently of the other. The upper gland packs the rodprimarily against the downward fiow of lubricating fluid and the lowergland packs the rod primarily against the upward how of the productionfluid, while each gland is effective against both upward and downwardflow in the event one or the other of the glands fails and allowsleakage.

The packing system also includes a vent 9dr; intermediate the two glandswhich allows bleed-off of the 1ubrieating fluid if the upper gland failsand bleed-off of the production fluid in the event that the lower glandfails, thus allowing the system to continue operation with failure ofone gland.

Each end of the housing has an enlarged recess therein so as toaccommodate packing rings between the walls of the recesses and thesurface of the rod 21 which passes through the housing. The packingrings are an expansi'ole type and upon compression thereof, are adaptedto tighten the seal between the housing and rod.

The rings 94 on the lower side of the housing for the low pressure glandmay be of a type known as U-shaped and may be stacked with spacer rings95 therebetween. The spacers'95 each have a circular projection which isadapted to fit between the legs of the Ll-shaped rings 94 and preventcollapse thereof. A pressure ring W bears against the lower surface ofthe lowermost ring 95.

An additional U-shaped ring 93 may be positioned between the rings 94and the inner end of the packing space. The ring 98 may be upwardly openand disposed between a spacer ring 99 which is in contact with theuppermost ring 94 and a spacer Mil. Tie spacer Tilt may have adownwardly extending circular projection Hill which prevents collapse ofthe legs of the ring '98.

The rings 102 which comprise the high pressure gland at the upper end ofthe housing may be of a V -shaped type and stacked in contact with oneanother so that compression of the series of rings causes the legsthereof to expand outwardly into sealing relation to the housing androd. The lowermost ring 102 bears against a spacer ring it)? which is incontact with a spacer ring the which bears against an inverted V-shapedring 135. The legs of the ring 1105 are held against collapse by a ring1% which bears against the shoulder defining the inner end of the upperrecess.

A pressure transmitting ring 167 bears against the uppermost ring 102.

Packing glands of the type defined by the rings 9 or rings 1% may becomeloose and tend to work longitudinally with respect to the housing due tothe reciprocation of the rod Zll. The movement of the rod causes africtional wearing of the packing and when the packing becomes worn andtends to work back and forth with the rod, the sealing efficiency of thepacking is seriously impaired.

In order to prevent such working of the packing the invention includes ameans which automatically compresses the rings to a fixed degree andmaintains a firm sealing engagement of the rings with the housing androd whenever wear on the rings impairs the seal. The means includespring biased latching members 163% and 109 which bear against the rings97 and 1&7 respectively. Coiled springs 116 and illll surround the rod21 and exert pressure on the members 108 and ms in packing tighteningdirections. The spring 110 may be seated on a washer assembly 112carried by a fixed latching member 113 while the upper end of spring 11bears against a washer assembly 114 carried by a fixed latching member115.

The latching members 108 and 169 are preferably of cup shape with aplurality of resilient arms diverging from the base thereof and the axisof the rod and members. The outer ends of the arms are adapted forengagement with a series of vertically spaced ratchet-like teeth ornotches formed in the inner walls of the members 113 and 115. The endsof the arms may ride over the teeth in an inward or packing tighteningdirection but cannot move outwardly.

The arrangement is such that the latching members 108 and M9 may moveinwardly under the bias of their associated springs but are preventedfrom return or outward movement. The springs Ill) and 111 are of suchstrength that they provide an initial compression of the packing rings.Further compression is provided by the pressure of the fluid which bearsagainst the packing. Whenever the rings become worn or loose, thepressure of the fluid will compress the rings and the springs 110 or 111as the case may be, will move their associated latching members MP8 or169 into firm back up relation to the packing. The compression of thepacking may be enhanced by the movement of the rod 21, since on theupstroke the friction between rod 21 and rings 94 and 98 tends to movethese rings into a more highly compressed state, while on the downstrokeof the rod 21, the frictional engagement tends to move the rings M2 and105 into a more highly compressed state. The effect is an automatictake-up or tightening of the packing followed by a positive locking ofthe packing in that position.

The packing gland at each end of the housing is thus confined between afixed stop on the housing and a movable stop comprised of the pressurering and latching mechanism, the movable stop being effective toautomatically take up the slack and further expand the rings foreffective sealing action thereof when such is required.

With this form of packing, the upper V-shaped rings effectively pack thepolish rod and prevent the high pressure lubricant from movingdownwardly along the rod while the U-shaped packing prevents theproduction fluid from contaminating the lubricant. If the upper ringsfor any reason leak lubricant under the high pressure or" the dash pot,such lubricant may run off through the vent 94M and down to the pump,thus minmizing a pressure build-up on the upper side of the lower rings.If the lower rings fail and allow leakage of the production fluidupwardly along the rod, such fluid may run off through vent 90a forreturn to the pump.

The assembly uses a control system which is particularly effective inallowing the use of relatively small motors, whi e providing adequatedriving power for the pumping unit. Energization and de-energization ofthe power input to the motor 34 is under control of a switch assemblygenerally designated at 120. The switch assembly is preferably mountedon the housing portion 29 as will be seen with reference to FIGURES land 3. In FIGURE 5, the switch assembly 120 is illustrated in rotatedrelation to the remainder of the assembly illustrated in Fl -SURE 5, theshowing of the switch assembly being removed from the rear portion ofthe housing portion 29 in FIGURE 5 so as to enable an understanding ofthe principles thereof. The switch assembly in cludes a toggle switch121 having an actuating member E22 which is movable between the twoextremes indicated in dotted outline in FIGURE 1. The actuating member122 is contacted intermittently during the operation of the system byswitch actuating arms 123 and 124 which are adjustably mounted inangular directions on a member 125. The member 125 is rotated by a shaft126 which carries a gear meshing with a gear 127 which is rotatable withthe driving member 3%. The gear arrangement is such that the shaft 126and member 125 are rotated through a partial revolution during therotation of the driving member 30 necessary to reciprocate the drivenmember 31 through the desired length of stroke. Thus, as the drivingmember 30 rotates in one direction during the lifting of the drivenmember 31, one member, such as the member 123, will move through thatpartial revolution necessary to engage the switch actuating member 122near the end of the lifting stroke of the member 31. When the member 30moves in the opposite direction, the member 125 is revolved in the opposite direction, so that near the end of the descending stroke of themember 31, the member 124 will contact the actuating member 122 andreverse the switch.

By adjusting the angular positions of the members 123 and 124, the timeor point in the stroke of member 31 at which the switch 121 is actuatedmay be adjusted in accordance with the desires of the user.

The system illustrated in FIGURE 1 is adapted to energize the motor 34after a. time interval immediately following the time when the member 31reaches the bottom of its stroke and thereafter hold the motor in theenergized condition until the driven member 31 reaches the top of itsstroke; whereupon the motor 34- is de-energized to allow a gravitationaldescent of the driven member 31. The controlling circuit isdiagrammatically illustrated in FEGURE 2. The system includes a timedelay mechanism 128 which becomes operative when the switch actuatingmember 122 closes the circuit thereto. The time delay mechanism mayinclude clock work or any suitable well known mechanism adapted to closea switch 128a after a selected time interval. After closing of theswitch 121 has been completed and after the selected time interval, thetime delay mechanism switch 128a completes a circuit to a relay 129 toclose the onoff motor sswitch 73d and energize the motor 34. When themotor 3 is energized it rotates the driving member 3% in such adirection as to cause elevation of the driven member 331. When thedriven member 31 reaches the top of its stroke, the switch actuatingmember 122 is contacted by one of the members, as for example the member124, to open this switch and thus break the circuit to the relay 129which holds the switch 13d in a closed position. When the motor 34 isde-energized, the weight of the driven member 3 1 and pumping unitattached thereto is sufiicient to cause the descent of the member 31,thereby causing opposite rotation of the member 3% and motor 34. Thisdescent of the member 31 continues until its final downward movement isretarded and checked by the dash pot assembly illustrated in FIGURE 6.At this point the other actuating member 123 reverses the switch 121 soas to again energize 9 the time delay mechanism to set up the motorcontrolling circuit for the elevation of the driven member 31.

The time delay may be an interval such that the pump has adequate timeto fill near the bottom or the stroke while allowing time for the motorto come to a complete stop before it is energized for the oppositedirection of rotation.

in order to prevent overheating of the driving assem-- bly, athermostatic switch or fuse 131 is in the circuit between switch 121 andtime delay mechanism 127. The thermostatic element 131 may have a heatsensing element 132 located in the lubricant reservoir so as to causeopening of the circuit whenever the temperature is above a predeterminedmaximum. Thus, if oil should leak from the reservoir with the resultthat the space within the housing heats up unduly, the element 131 willstop operation of the actuator, thus allowing the system to fail safely.Furthermore, it should be noted that it the packing glands become undulyheated, the heat there of will be transmitted to the lubricant with theresult that lubricant may heat to a temperature causing opening of thecircuit. Thus the element 131 protects both the transmission and packinggland against overheating.

FIGURE 8 illustrates a further embodiment of the invention. In thisembodiment, the housing is shown at 140 and houses a driving member 141and driven memher 142 of the same character as the driving and drivenmembers 3% and 31 of FIGURE 1. A motor 143 is mounted on an enlargedintermediate portion of the housing and supplies power to the drivemember Mil through bevel gears 14 i and 145. The driving member 141 andgear 144 may be supported by bearings M in a manner similar to thesupport of the similar elements in FIG- URES 1 and 5. in this embodimentof the invention the motor 144 is controlled through a time delay system147 which, includes a reversing switch mechanism generally designated at14-8. The switch mechanism 1 .48 is similar to the switch assembly 12dof FlGURE l and is actuated in response to rotation of the drivingmemher 141.

in the system of FlGURE 8, the upper end of the driven member carries apiston 14% which is slideably mounted in a cylinder J. The cylinder 15bis positioned within the upper portion 15% of the housing. A supportingplate 151 may be mounted on the portion of the housing surrounding thetransmission to provide support for the lower end of the cylinder 1% andupper housing wall. The plate 151 includes apertures and leading into anair jacket surrounding the cylinder 1%. Gil may be maintained in thecentral portion of the housing to a level generally corresponding to alevel slightly above the level of the gear T l i l as may be indicatedfrom time to time by the oil level gauge 15 in this embodiment, theportion of the housing space above the level of oil is filled with airunder pressure as through an air inlet As the driven member M2 andpiston $.49 move downwardly, the air within the housing is furi161compressed, thus retarding the downward movement 1" the driven member 14pump. The pressure may maintained at a level such that the total loadimposed on the motor 14 during the down stroke of the member 14?. isgenerally equal to the load on the motor during the upward stroke.

The upper wall 15 of the housinp includes a ertures is adapted to befixed to a w ich is similar to the produc- The production mansplinedguide is proat a position within the casing 160. As will be seen best inFIGURE 10, the lower of the driven member 142 carries a splined guideblock lei which has grooves therein which receive splincd ribs 162 onthe tubing 163. The guide lock 161 may be keyed to the lower end of thedriven member ltd-Z and held thereon as by means of nuts 164. The polishrod T for the pump may be threaded into the lower end of the drivenmember 142.

in order to lubricate the cylinder 15%, the spline block 161 hastransverse passages 16in. therein which feed lubricant from the exteriorof the block to a longitudinally extending passage loll) in the drivenmember 142 so that during descent of the spline block 161, lubricant isforced upwardly through the screw for discharge through feed passages1610 in the piston 149.

A production passage is provided between the tubing 163 and a secondtube 166, which tube 166 is spaced inwardly from the casing 16b todefine a gas passage therebetween.

It should be understood that a packing means, which may take the form ofthe packint illustrated in PEG- URE 7, may be fixed with respect to thetube 163 at a level beneath the lowermost point of travel of the splinedguide.

The system of FlGURES 8, 9 and it) utilizes a time delay in the motorcontrol system at each limit of movement of the driven member 242. Thecontrol unit 147 includes a reversing switch 17% for the motor. Thecircuit for the system, which is diagrammatically illustrated in FIGURE9, includes a pair of time del y mechanisms in parallel with one anotherand diagrammatically indicated at 171 and 372. The time dela mechanismsreceive power from a transformer 1710. which alternately supplies powerto one or the other of the mechanisms as switch 148 is moved from oneposition to the other. One time delay mechanism 173 is actuated when thedriven member M2 nears the end of its upper limit of movement and causesactuation of the switch member 1'73 in one direction, as by means of therotatable switch actusting member 174 which driven from the drivingmember 1 53 in a manner similar to the driving of the switch member 25in FIGURE 1. Conversely, when the driven member nears the end of itslower limit of movement, the switch actuating member 173 is snapped tothe opposite position.

The arrangement is such that near the upper limit, the switch 173 opensthe motor circuit and energizes the time delay mechanism 171, whichcloses a switch lla to ene a relay l7a after a predetermined interval oftime, to thereby reve se the switch li t) and thus reverse movement ofthe rotor lie -i to ca se descent of the driven member When the drivenmember 142 a; preaches the bottom limit of movement, the switch mem er 3is moved to the opposite position, thus opening the motor circuit andenergizing the time delay mech sin 172 which, after a predeterminedinterval or" time, closes a switch 176 to energize a relay coil 176a toreverse the switch 176* for rotation of the motor 144 in the oppositedirection and to cause elevating movement of the driven membe 142.

Thus when the driven member 142 approaches either limit of movement, themotor current is discontinued to allow the motor to coast to a completestop without need of any plugging of the moto Actuation of the switchbreaks the circuit to the motor and set" up the motor control circuitfor the reverse movement.

A heat sensitive member 1% is responsive to the heat of the lubricatingreservoir as by a sensing element E31 for breaking the circuit fromswitch 3148 when the heat in the region of the transmission reaches anexcessive amount thus providing safety as in the system of Fi URE 1.

it should be understood that the switch actuating blades 173 and 179 areso angularly related to the center oi rotation of the member F.7d thatthe circuit to the motor is broken at a point before the limit ofmovement desired so that the motor, in effect, may coast to the finallimit.

Where as the drawings illustrate motors coupled to the driving membersthrough the use of fluid couplings, it should be understood that othercoupling arrangements could be used. Furthermore, it should beunderstood that the pinion gears illustrated in FIGURES 1 and 8 can bedriven by means of a motor away from the housing and interconnected withthe pinion 145 through the use of suitable belt or chain transmissionsor the like.

The actuators herein illustrated and described are easily fitted to thecasing head of existing wells as by coupling the actuator housing to thecasing head.

The actuators are particularly well suited for situations requiring longoperating strokes. The actuators may be used with quite a variety ofdifferent lengths of pumping strokes, the reciprocating driven memberand housing being made sufficiently large to accommodate the maxi mumstroke desired in any particular situation. The actuators areparticularly efficient in the transmission of power from the prime moverto the sucker rod. In this regard the bevel gear and particular screwand nut transmission utilized are highly efficient in that power lossesdue to friction in the transmission are held to a minimum. Intransmitting the power from the prime mover to the reciprocating rod inany installation, the length of stroke is easily adjusted in accordancewith the desires of the user by simply adjusting the angular position ofthe actuating member of the toggle switch assemblies to thus adjust theupper limit of travel of the driven member.

In each form of the invention described, namely the embodiment of FIGURE1 and the embodiment of FIG- URE 8, the down stroke of the reciprocatingdriven member is retarded near the end of its stroke so as to slow downthe downward movement of the sucker rod and allow the motor andtransmission to coast to a stop against the cushion of fluid in the dashpot of FIGURE 1 or the air cylinder of FIGURE 8.

The switch actuating members are preferably so adjusted that theyactuate their associated switches prior to the time that the end of thereciprocating stroke is reached. In the case of the embodiment of FIGURE1, for example, the switch may be actuated sometime after the pistonenters the tapered dash pot cylinder. Actuation of the switch energizesthe time delay mechanism and the time interval between actuation of theswitch and energization of the motor may be such that when the motorfinally comes to rest, the driven member may stay at this lower positionfor a short period of time sufiicient to enable the pump cylinder tofill before the motor is energized to commence the upward stroke. Duringupward movement the toggle switch is again actuated to shut off thecurrent to the motor prior to the time that the driven member reachesthe upper limit of travel so that the motor will spin to a stop againstthe weight of the sucker rod and driven member. When the upper limit isreached, the weight of the sucker rod and driven member are sufficientto cause them to descend and in the course of such descent the drivingmember and motor will be rotated in the opposite direction.

In the embodiment illustrated in FIGURES 8 and 9, the toggle switch 170is actuated to break the current to the motor prior to the time that thedriven member reaches either its lower limit of travel or its upperlimit of travel. Actuation of the toggle switch at either limit oftravel breaks the circuit to the motor and the motor gradually costs toa stop. The toggle switch at the same time energizes the time delaymechanism so that after a predetermined interval of time followingactuation of the toggle switch, the reversing switch is reversed and themotor is again energized for the stroke in the opposite direction.

In the system of FIGURE 8, the time interval between de-energization ofthe motor and consequent reversing thereof at the upper end of thestroke may be such that it is only slightly greater than the timenecessary to allow the motor to come to a complete stop.

It should be noted that the system of FIGURE 1 allows the motor to coastto a stop after actuation of the limit switch which occurs prior to thetime that the actuator reaches the upper limit of travel. When the motorcomes to a stop at the end of this stroke, the driven member 31 willstart to descend slowly. Thus the time interval occurring after themotor is de-energized and during the final coasting of the motor andduring the slow initial portion of the descent of member 31 will be suchas to provide a well filling time interval, or time for the productionfluid to flow into the well.

In the system of FIGURE 8 the time interval at the top of the stroke maybe varied to suit individual installations, as by suitable adjustment ofthe time delay mechanism in the circuit of FIGURE 9.

The controlling circuits for the actuators are highly adaptable to fullyautomatic operation as by means of program control systems or the liketo turn the actuators on and off for predetermined periods of operation.

Whereas, I have shown and described an operative form of my invention, Iwish it to be understood that this showing is to be taken in anillustrative or diagrammatic sense only. There are many modifications tothe invention which will be apparent to those skilled in the art andwhich will fall within the scope and spirit of the invention. The scopeof the invention should be limited only by the scope of the hereinafterappended claims.

I claim:

1. A reciprocating pump actuating system including a reciprocating pumpactuating member adapted at one end of its stroke to allow filling of apump actuated thereby, a prime mover in driving relation to saidactuating member, means retarding movement of said actuating member asit approaches said end of its stroke, control means for causingoperation of said prime mover for reverse travel of said actuatingmember at said end of its stroke, time delay means delaying operation ofsaid control means when said member is at said end of its stroke so asto provide a pump filling time interval, and means terminating operationof said prime mover prior to the time that said member reaches the otherend of its stroke to thereby allow said member and prime mover to coastto a stop at said other end of the members stroke.

2. The system of claim 1 wherein said member reciprocates vertically anddescends to said pump filling end of stroke by gravity, the prime moverbeing driven by said member in a de-energized state during said descent.

3. The system of claim 1 wherein said member reciprocates vertically andsaid prime mover drives said member in each stroke direction of saidmember, said control means including means for reversing said primemover for reverse operation of said member at each end of the stroke ofsaid member.

4. The system of claim 1 wherein said retarding means includes ahydraulic dash pot associated with said mem- 5. The system of claim 1wherein said retarding means includes an air counterbalance associatedwith said member and adapted to compress air as said member reaches saidend of its stroke.

6. In a reciprocating pump actuating mechanism, a reciprocable drivenmember and a rotatable driving member in engagement therewith andadapted during rotation thereof to reciprocate said driven member, motormeans for rotating said driving member, switch means for energizing andde-energizing said motor means, switch actuating means driven by saiddriving member for actuating said switch at predetermined points in thereciprocatng travel of said driven member, said switch means beingadapted to energize said motor means for reverse move- 13 ment thereof,and time delay means delaying operation of said motor for apredetermined interval of time after actuation of said switch means,said time delay means being effective to delay energization of saidmotor and reciprocation of said driven member at each limit of travel 5of said driven member.

7. The system of claim 6 characterized by and including heat responsivemeans for de-energizing said motor upon the occurrence of apredetermined elevated temperature in the region of said driven memberand said driving 10 member.

References Cited in the file of this patent UNITED STATES PATENTS1,428,300 Scharpenberg Sept. 5, 1922 15 14 Jackson Mar. 9, Wild Jan. 21,Geary Nov. 28, Brassel May 16, Benson Aug. 15, Hanson Apr. 5, WilliamsMay 31, Williamson Oct. 11, Wright Sept. 9, Shields Jan. 10, LindseyNov. 25, Gillum Nov. 24,

